EP1912836B1 - Systeme de freinage electrohydraulique pour vehicules automobiles - Google Patents

Systeme de freinage electrohydraulique pour vehicules automobiles Download PDF

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Publication number
EP1912836B1
EP1912836B1 EP06792661A EP06792661A EP1912836B1 EP 1912836 B1 EP1912836 B1 EP 1912836B1 EP 06792661 A EP06792661 A EP 06792661A EP 06792661 A EP06792661 A EP 06792661A EP 1912836 B1 EP1912836 B1 EP 1912836B1
Authority
EP
European Patent Office
Prior art keywords
pressure
master cylinder
brake
hydraulic
electrohydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP06792661A
Other languages
German (de)
English (en)
Other versions
EP1912836A1 (fr
Inventor
Peter Rieth
Lothar Schiel
Stefan Drumm
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Publication of EP1912836A1 publication Critical patent/EP1912836A1/fr
Application granted granted Critical
Publication of EP1912836B1 publication Critical patent/EP1912836B1/fr
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4072—Systems in which a driver input signal is used as a control signal for the additional fluid circuit which is normally used for braking
    • B60T8/4081—Systems with stroke simulating devices for driver input

Definitions

  • the invention relates to an electrohydraulic brake system for motor vehicles, of the type "brake-by-wire" according to the preamble of patent claim 1.
  • An electro-hydraulic brake system is z. B. from the international patent application WO 03/047936 known.
  • the prior art brake system includes hydraulic means which, in an emergency or fallback mode characterized by a failure of electrohydraulic components, apply a hydraulic pressure present in the high pressure accumulator to release the brake fluid in the "brake-by-wire" mode from the previous normal brake application Master cylinder has been displaced in the path simulator, to provide for a mechanical-hydraulic auxiliary braking available by a hydraulic valve controlled switching the high-pressure accumulator pressure on a connected in normal operation with the brake fluid reservoir hydraulic space of the travel simulator pressure medium from a connected to the master cylinder hydraulic space of the travel simulator is displaced in the master cylinder and an auxiliary brake circuit connected thereto, so that the wheel brakes are actuated with a hydraulic pressure, which is determined by the muscle power of the driver is, with which this actuates the brake pedal.
  • a disadvantage is felt in the prior art brake system the fact that in case of failure of the electro-hydraulic components only a deceleration of the vehicle with a brake pressure far below the value achieved in the "brake-by-wire" mode with the same operating force is possible.
  • a brake booster with wheel brake pressures above the pressure applied by the driver with the brake pedal in the master cylinder pressure can not be displayed without fully functional electro-hydraulic components.
  • it is considered to be disadvantageous that caused by the mentioned sudden return of pressure medium from the travel simulator in the master cylinder reactions to the brake pedal, which are likely to irritate the driver in addition to the loss of brake boosting.
  • a generic brake system is for example from the WO 98/26966 A refer to.
  • the valve assembly described therein is both hydrally actuated by the master cylinder and electromagnetically.
  • electro-hydraulic means are formed by analog controllable solenoid valves, which are hydraulically connected to the pressure source and the pressure medium reservoir.
  • adjustable solenoid valves have already proven themselves as brake system components. Also in the prior art brake system they are included, albeit elsewhere and in other function.
  • valve assembly is effected by means of an actuating element which is in force-transmitting connection with a valve body of the valve arrangement.
  • a hydraulically effective cross-sectional area of the actuator defines the proportionality factor between the master cylinder pressure and the transmitted valve actuation force.
  • the valve assembly is designed as a slide valve.
  • the slide valve has the advantage of a one-piece construction.
  • the above-mentioned actuator is executed in a further embodiment of the subject invention as a hydraulic piston, which is provided both with the pressure provided by the master cylinder pressure and with the electrically analog controllable pressure can be applied.
  • the hydraulic piston preferably defines a hydraulic space that can be acted upon by one of the provided pressures.
  • Another useful development of the invention is to insert in the connections between the master cylinder and the hydraulic chamber and between the pressure source and the hydraulic chamber, a shuttle valve, which is actuated by a pressure difference between the pressure provided by the master cylinder and the electrically controllable pressure.
  • the hydraulic actuation of the shuttle valve is carried out such that the hydraulic space is acted upon by the respective higher pressure. This automatically switches between the "brake-by-wire" mode and the hydraulically amplified mode so that the higher brake pressure demand prevails.
  • the hydraulic piston is designed as a stepped piston whose annular surface can be acted upon by the pressure provided by the master cylinder, while the piston surface of smaller diameter can be acted upon by the electrically analog controllable pressure.
  • the hydraulic piston can be dispensed with a shuttle valve to select the respective higher Radbremsdruckan Kunststoff.
  • a further advantageous embodiment of the subject invention provides that in the connections between the master cylinder and the wheel brakes and between the valve assembly and the wheel change valves are inserted, which by a pressure difference between the pressure provided by the master cylinder and the output from the valve assembly, analog controllable hydraulic Brake pressure to be actuated and connect the master cylinder to the wheel brakes in a first switching position and connect the output of the valve assembly with the wheel brakes in a second switching position.
  • the electro-hydraulic brake system shown only schematically in the drawing consists essentially of an actuatable by means of a brake pedal 1, two-circuit hydraulic pressure generator or master cylinder 2 in tandem design, cooperating with the tandem master cylinder 2 way simulator 3, a tandem master cylinder 2 associated pressure fluid reservoir 4, a schematically illustrated Hydraulic module 5, to which the vehicle wheels associated wheel brakes 7, 8, 11, 12 are connected, and an electronic control unit 16.
  • a hydraulic control unit HCU 6 all, for individual wheel Contains pressure control operations required components or pressure control valves, a provided with the reference numeral 13 valve assembly and two shuttle valves 17, 18 integrated, whose task will be explained below.
  • To determine the speed of the vehicle wheels are merely indicated, not nearer designated wheel sensors.
  • the known per se tandem master cylinder 2 has two pistons 9, 10, limited, separate pressure chambers 14, 15 which are connectable both with the pressure medium reservoir 4 and via the HCU 6 with the vehicle brakes 7, 8, 11, 12.
  • the above-mentioned pressure source is formed by a motor-pump unit 20, which consists of an electric motor 22 and a driven by the electric motor 22 pump 23, a pump 23 in parallel pressure relief valve 24 and a high-pressure accumulator 21 can be charged by the pump 23.
  • the present in the high-pressure accumulator 21 hydraulic pressure is monitored by a pressure sensor 25.
  • valve assembly 13 which is formed in the example shown as a slide valve, is operatively connected between the pressure source 20, 21 and the wheel brakes 7, 8, 11, 12 and on the one hand by an electromechanical actuator 28 and on the other hand by the first pressure chamber 14 of the master cylinder 2 actuated hydraulic pressure actuated.
  • the wheel brakes 7, 8 are connected to the first pressure chamber 14 by means of a line 26, in which the first shuttle valve 17 is inserted, which connects the first pressure chamber 14 with the wheel brakes 7, 8 in a first switching position and in the second switching position connects the output of the valve assembly 13 with the wheel brakes 7, 8 with simultaneous interruption of the line 26.
  • the shuttle valve 17 branches off the line 26 another, leading to the valve assembly 13 line 27 from which serves the hydraulic control of the valve assembly 13.
  • the shuttle valve 17 is actuated by a pressure difference between the pressure provided by the master cylinder 2 and the pressure of the valve assembly 13 analog controllable hydraulic brake pressure.
  • This actuation of the shuttle valve 17 is carried out such that the wheel brakes 7, 8 are acted upon by the respective higher pressure.
  • the pressure introduced in the first pressure chamber 14 is monitored by means of a pressure sensor 19, while the pressure supplied by the valve arrangement 13 is detected by means of a pressure sensor 29. Accordingly, the above explanations also apply to the second pressure chamber 15, the second shuttle valve 18 and the wheel brakes 11, 12 connected to the second pressure chamber 15.
  • the above-mentioned electronic control and control unit 16 the output signals of the pressure sensors 19, 25, 29, the wheel speed sensors and a preferably redundant executed braking request detection means 35 are supplied, which is associated with the master cylinder 2, serves to control the motor-pump unit 20th , the actuator 28, and the hydraulic control unit HCU 6.
  • valve assembly 13 a valve body 30 which, in the switching position shown, a hydraulic connection between an output space 31 which is connected by a line 34 to an input port of the shuttle valve 17, and a hydraulic chamber 32 allows, with the Pressure medium reservoir 4 is in communication.
  • the chamber 32 is bounded by a hydraulic piston 33, on the one hand, as already mentioned above, charged via the line 27 with the pressure applied in the master cylinder 2 pressure and on the other hand is in force-transmitting connection with the electromechanical actuator 28.
  • valve assembly 13 in addition to the hydraulic control by the master cylinder 2 driven by electro-hydraulic means, which are formed in the example shown by electrically controllable, analog controllable 2/2-way valves 35, 36.
  • the connected to the output of the pressure source 20 and 21 2/2-way valve 35 is designed as normally closed (SG -) - valve, while the other 2/2-way valve 36 is formed as a normally open (SO) valve.
  • SO normally open
  • the output side of the first-mentioned valve 35 and the input side of the second-mentioned valve 36 is connected to a hydraulic chamber 37, which is bounded on the one hand by the piston 33 and on the other hand by a further piston 38.
  • the pressure in the chamber 37 which is controlled electrically analogously by the valves 35, 36, is monitored by means of a further pressure sensor 39.
  • the piston 33 is formed as a stepped piston whose annular surface 40 is acted upon by the pressure provided by the master cylinder 2, while acting on its piston surface 41 of smaller diameter of the electrically controlled by the 2/2-way valves 35, 36 pressure.
  • the other piston 38 is biased by a compression spring 42, wherein its movement against the force of the spring 42 allows an enlargement of the hydraulic space 37 and thus a recording of the valves 35, 36 provided pressure medium volume.
  • a Shuttle valve 43 inserted, which can be actuated by a pressure difference between the pressure provided by the master cylinder 2 and the output of the electro-hydraulic means 35, 36, electrically controlled analog hydraulic pressure.
  • the actuation of the shuttle valve 43 is performed such that the piston 33 is acted upon by the respective higher pressure.
  • a volume receiving element 44 is connected to the aforementioned line.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Claims (12)

  1. Système de freinage électrohydraulique pour véhicules automobiles, du type "Brake-by-Wire", comprenant un cylindre de frein principal (2) pouvant être actionné au moyen d'une pédale de frein (1), présentant au moins un espace de pression (14, 15), un réservoir de fluide sous pression sans pression (4), un simulateur de course (3) coopérant avec le cylindre de frein principal (2), qui, en mode de "Brake-by-Wire", donne au conducteur du véhicule la sensation usuelle sur la pédale de frein (1),
    une source de pression hydraulique (20, 21) commandable au moyen d'une unité de commande et de régulation électronique (16), qui est formée d'une pompe hydraulique (23) ainsi que d'un accumulateur haute pression (21) pouvant être chargé par la pompe (23) et avec la pression duquel des freins de roue (7, 8, 11, 12) du véhicule peuvent être sollicités,
    lesquels sont raccordés au cylindre de frein principal (2) au moyen d'au moins une connexion verrouillable par une soupape de coupure, et auxquels sont associées des soupapes de régulation de la pression qui peuvent être commandées par l'unité de commande et de régulation électronique (16), un agencement de soupape (13) étant prévu dans la connexion entre les freins de roue (7, 8, 11, 12) et la source de pression (20, 21), lequel peut être actionné à la fois hydrauliquement par la pression fournie par le cylindre de frein principal (2) et aussi par une force extérieure, caractérisé en ce que pour appliquer la force extérieure, des moyens électrohydrauliques (35, 36) sont prévus, lesquels produisent une pression commandable de manière analogique électriquement.
  2. Système de freinage électrohydraulique selon la revendication 1, caractérisé en ce que les moyens électrohydrauliques sont formés par des électrovannes réglables de manière analogique (35, 36), qui sont connectés hydrauliquement à la source de pression (20, respectivement 21) et au réservoir de fluide sous pression (4).
  3. Système de freinage électrohydraulique selon la revendication 2, caractérisé en ce que l'actionnement de l'agencement de soupape (13) s'effectue au moyen d'un élément d'actionnement (33), qui est en liaison par transmission de force avec un corps de soupape (30) de l'agencement de soupape (13).
  4. Système de freinage électrohydraulique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'agencement de soupape (13) est réalisé sous forme de soupape à tiroir.
  5. Système de freinage électrohydraulique selon la revendication 3 ou 4, lorsqu'elle dépend de la revendication 3, caractérisé en ce que l'élément d'actionnement (33) est réalisé sous forme de piston hydraulique qui peut être sollicité à la fois par la pression fournie par le cylindre de frein principal (2) et par la pression commandable de manière analogique électriquement.
  6. Système de freinage électrohydraulique selon la revendication 5, caractérisé en ce que le piston hydraulique limite un espace hydraulique (37, 37a) qui peut être sollicité par l'une des pressions fournies.
  7. Système de freinage électrohydraulique selon la revendication 6, caractérisé en ce que dans les connexions entre le cylindre de frein principal (2) et l'espace hydraulique (37a), ainsi qu'entre la source de pression (20, respectivement 21) et l'espace hydraulique (37a), est insérée une soupape d'échange (43) qui est actionnée par une différence de pression entre la pression fournie par le cylindre de frein principal (2) et la pression commandable de manière analogique électriquement.
  8. Système de freinage électrohydraulique selon la revendication 7, caractérisé en ce que l'actionnement hydraulique de la soupape d'échange (43) s'effectue de telle sorte que l'espace hydraulique (37a) soit sollicité à chaque fois avec la pression la plus élevée.
  9. Système de freinage électrohydraulique selon l'une quelconque des revendications 5 à 8, caractérisé en ce que le piston hydraulique (33) est réalisé sous forme de piston étagé, dont la surface annulaire (40) est sollicitée par la pression fournie par le cylindre de frein principal (2), tandis que sa surface de piston (41) de plus petit diamètre est sollicitée par la pression pouvant être commandée de manière analogique électriquement.
  10. Système de freinage électrohydraulique selon l'une quelconque des revendications 6 à 9, caractérisé en ce que l'espace hydraulique (37) est limité d'autre part par un autre piston (38) précontraint au moyen d'un ressort (42), dont le mouvement à l'encontre de la force du ressort (42) permet une réception d'un volume pour le fluide sous pression délivré par les moyens électrohydrauliques (35, 36).
  11. Système de freinage électrohydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que dans les connexions (26, -) entre le cylindre de frein principal (2) et les freins de roue (7, 8, 11, 12) ainsi qu'entre l'agencement de soupape (13) et les freins de roue (7, 8, 11, 12), sont insérées des soupapes d'échange (17, 18) qui sont actionnées par une différence de pression entre la pression fournie par le cylindre de frein principal (2) et la pression de freinage hydraulique commandable de manière analogique fournie par l'agencement de soupape (13), et qui relient dans une première position de commutation le cylindre de frein principal (2) aux freins de roue (7, 8, 11, 12) et dans une deuxième position de commutation la sortie de l'agencement de soupape (13) aux freins de roue (7, 8, 11, 12).
  12. Système de freinage électrohydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que dans les connexions hydrauliques entre lé cylindre principal (2) et les freins de roue (7, 8, 11, 12) sont insérées des soupapes à 2/2 voies actionnables électriquement (45, 46), qui, dans le cas d'une activation empêchent un échange de fluide sous pression entre le cylindre de frein principal (2) et les freins de roue (7, 8, 11, 12) ainsi qu'entre le cylindre de frein principal (2) et l'agencement de soupape (13).
EP06792661A 2005-08-02 2006-08-02 Systeme de freinage electrohydraulique pour vehicules automobiles Ceased EP1912836B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005036233 2005-08-02
DE102006015906A DE102006015906A1 (de) 2005-08-02 2006-04-05 Elektrohydraulische Bremsanlage für Kraftfahrzeuge
PCT/EP2006/064986 WO2007014962A1 (fr) 2005-08-02 2006-08-02 Systeme de freinage electrohydraulique pour vehicules automobiles

Publications (2)

Publication Number Publication Date
EP1912836A1 EP1912836A1 (fr) 2008-04-23
EP1912836B1 true EP1912836B1 (fr) 2009-12-16

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Application Number Title Priority Date Filing Date
EP06792661A Ceased EP1912836B1 (fr) 2005-08-02 2006-08-02 Systeme de freinage electrohydraulique pour vehicules automobiles

Country Status (5)

Country Link
US (1) US20100259096A1 (fr)
EP (1) EP1912836B1 (fr)
JP (1) JP4944110B2 (fr)
DE (2) DE102006015906A1 (fr)
WO (1) WO2007014962A1 (fr)

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JP5819359B2 (ja) * 2013-07-16 2015-11-24 本田技研工業株式会社 電動ブレーキ装置
JP6413138B2 (ja) 2015-02-06 2018-10-31 日立オートモティブシステムズ株式会社 液圧制御装置及びブレーキシステム
JP6432484B2 (ja) * 2015-10-20 2018-12-05 株式会社アドヴィックス 車両の制動制御装置
DE102017203952A1 (de) 2017-03-10 2018-09-13 Continental Teves Ag & Co. Ohg Fahrzeugbremsanlage mit einem pedalbetätigten Hauptbremszylinder
DE102017218384B4 (de) 2017-10-13 2020-03-26 Bayerische Motoren Werke Aktiengesellschaft Verfahren zum Betreiben eines Fahrzeuges mit einem elektrohydraulischen Bremssystem
DE102018206586B4 (de) * 2018-04-27 2020-06-25 Bayerische Motoren Werke Aktiengesellschaft Verfahren zum Betreiben eines Fahrzeuges mit einem elektrohydraulischen Bremssystem sowie elektrohydraulisches Bremssystem eines Fahrzeuges
US11932213B2 (en) * 2021-03-26 2024-03-19 Toyota Research Institute, Inc. System and method for controlling one or more brakes of a vehicle
US11396917B1 (en) 2021-03-29 2022-07-26 Toyota Research Institute, Inc. System and method for controlling a clutch plate assembly of a vehicle
US20220371562A1 (en) * 2021-05-24 2022-11-24 Bwi (Shanghai) Co., Ltd. Brake-by-wire system with pressure balanced psu piston
DE102021114621A1 (de) 2021-06-08 2022-12-08 Bayerische Motoren Werke Aktiengesellschaft Fahrzeug mit einem Bremssystem
DE102021114622A1 (de) 2021-06-08 2022-12-08 Bayerische Motoren Werke Aktiengesellschaft Fahrzeug mit einem Bremssystem

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Also Published As

Publication number Publication date
WO2007014962A1 (fr) 2007-02-08
EP1912836A1 (fr) 2008-04-23
DE102006015906A1 (de) 2007-07-26
JP4944110B2 (ja) 2012-05-30
US20100259096A1 (en) 2010-10-14
JP2009502645A (ja) 2009-01-29
DE502006005670D1 (de) 2010-01-28

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